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US20150275931A1 - Turbine valve actuator - Google Patents

Turbine valve actuator Download PDF

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Publication number
US20150275931A1
US20150275931A1 US14/443,690 US201314443690A US2015275931A1 US 20150275931 A1 US20150275931 A1 US 20150275931A1 US 201314443690 A US201314443690 A US 201314443690A US 2015275931 A1 US2015275931 A1 US 2015275931A1
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US
United States
Prior art keywords
pressure
medium space
valve actuator
actuating part
turbine valve
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Granted
Application number
US14/443,690
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US10066645B2 (en
Inventor
Kristof Schlemmer
Martin Piechnick
Wolfgang Britz
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Hydac System GmbH
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Hydac System GmbH
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Assigned to HYDAC SYSTEM GMBH reassignment HYDAC SYSTEM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRITZ, WOLFGANG, PIECHNICK, MARTIN, SCHLEMMER, Kristof
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16—Control of working fluid flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1476—Special return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F15B2201/4155—Gas ports having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31505—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and a return line
    • F15B2211/31511—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and a return line having a single pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/765—Control of position or angle of the output member
    • F15B2211/7656—Control of position or angle of the output member with continuous position control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7716—Control of direction of movement of the output member with automatic return
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8633—Pressure source supply failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode

Definitions

  • the invention relates to a turbine valve actuator for controlling at least one valve unit of a medium-operated consumer unit, such as a steam or gas turbine, having an actuating part drive that comprises a movable actuating part, at least one first medium space, and at least one second medium space, wherein a pressure build-up in the first medium space attempts to cause a movement of the actuating part in a first direction and a pressure build-up in the second medium space attempts to cause a movement of the actuating part in an opposing second direction, wherein the first medium space can be supplied with a fluid in predeterminable amounts by means of a supply device and the second medium space is acted upon by an energy accumulator.
  • a medium-operated consumer unit such as a steam or gas turbine
  • Such turbine valve actuators are known in the prior art, e.g., from patent document DE 10 2004 042 891 B3.
  • a turbine valve actuator is constituted of a hydraulic working cylinder, wherein a piston rod unit is permanently spring-loaded, preferably by a packet of Belleville washers.
  • the piston rod unit is held against the compressive force of the Belleville washers via the system pressure of a fluid circuit in a retracted position.
  • the piston rod unit extends from the working cylinder, and a control valve is activated, which controls a medium flow to a consumer unit and, in this case, stops a mass flow of steam for the driving of a steam or gas turbine.
  • the invention addresses the problem of providing an improved turbine valve actuator with which subsequent adaptation to other steam valves is possible.
  • the energy accumulator is at least one hydraulic accumulator provided with a pre-load pressure, which is permanently connected to the second medium space.
  • the basis of the turbine valve actuator according to the present invention is the use of at least one hydraulic accumulator in order to control same.
  • the turbine valve actuator can therefore be connected to a wide range of valve units.
  • the advantageous use of piston accumulators as standard components also contributes to reducing costs.
  • Hydraulic accumulators are distinguished by the possibility of the adjustability of the characteristics thereof.
  • the use of hydraulic accumulators that are external, i.e., arranged outside the medium spaces, makes it possible to employ interchangeable components and thus supports the modularization and adaptability of the turbine valve actuator. Another advantage is that the actuating part drive can be operated in a nearly force-free manner for installation and maintenance.
  • the actuating part drive is configured as a hydraulic motor or hydraulic working cylinder, in a preferred embodiment, the first medium space forms a rod working space in the hydraulic working cylinder, and the second medium space forms a piston working space within a cylinder housing, the spaces formed being separated from one another by a piston rod unit as an actuating part.
  • Such working cylinders are readily available on the market as linear cylinders in a variety of embodiments. For the purposes of modularization, they can be used as standard components. This contributes to considerable cost savings in manufacturing.
  • the working cylinder is equipped with an end position damping in the direction of extension.
  • the piston rod unit either retracts or extends due to the fluid pressure of the hydraulic accumulator, relative to the cylinder housing, if the fluid pressure drops in the first medium space.
  • the fluid pressure is to be maintained in the first medium space if the valve unit is to be opened. If, however, the fluid pressure drops in the first medium space for any reason, e.g., because of a failure in the supply device or due to targeted release via a safety valve, then without intervention, this leads to a closing of the valve unit and thus to the shutting off of a media flow to a consumer unit downstream of the valve unit.
  • a pressure-adjusting device can be provided.
  • This pressure-adjusting device makes it possible for the fluid pressure in the second medium space to be adjusted between a minimum pressure and a maximum pressure in such a manner that the actuating part moves in the unpressurized first medium space in the second direction to an end position, wherein an exceeding of the allowable driving forces is prevented.
  • the pressure-adjusting device consequently maintains the functional readiness of the turbine valve actuator in ongoing operation.
  • the pressure at which the actuating part is acted upon is advantageously coordinated to the downstream valve unit, thus ensuring that same is closed if there is a pressure drop in the first medium space. Due to the pressure-adjusting device, an overload protector for the valve unit is also provided, because excess pressures in the second medium space can be prevented by releasing the fluid.
  • the pre-load pressure can also be adjusted on a gas side of the hydraulic accumulator, by using a pre-load adjustment device. Adjusting the pre-load pressure makes it possible to adjust different spring characteristics or pressure levels for these spring characteristics.
  • a positioning device, the pressure adjustment device, and/or the pre-load adjustment device preferably receive position set-point targets or actual position values for the respective medium spaces from a central or remote controller, so that different force-stroke characteristics of the actuating part can be realized, and preferably can be altered during operation of the turbine valve actuator. These targets can also be provided from a control room in running operation.
  • safety devices known in the prior are only able to produce degressive characteristics through Belleville washers
  • the turbine valve actuator according to the invention now makes it possible to produce progressive, linear, constant (isobaric), or even regressive force-stroke characteristics.
  • the pressure consumed from the hydraulic accumulator as an energy accumulator can be adjusted to a nearly constant level via the traveling of the actuating part, wherein different pressure levels can be advantageously selected.
  • the pressure of the actuating part can be determined by means of a preferably integrated and/or redundant displacement measurement device, and thus the desired pressure can be defined in the second medium space.
  • the displacement measurement here makes it possible, in a particularly simple manner, to monitor the turbine valve actuator.
  • sensors for measuring the pressure and/or temperature can be provided at the second medium space.
  • the supply device for the first medium space in an actuating drive, comprises a pressure-controlled axial piston pump having a swivel angle adjustment, or, in a switching drive, comprises a gear pump having a constant delivery volume.
  • the supply device cooperates with the positioning device. If the supply device comprises an axial piston pump, then a proportional valve is provided in the positioning device. If the supply device comprises a gear pump, then the positioning device has a control valve. To conserve energy, the gear pump can be switched off after a desired pressure is reached and switched on only when needed (accumulator charging).
  • the supply device may further comprise an additional hydraulic accumulator as a part of an accumulator charge circuit.
  • the volume accumulated in the additional hydraulic accumulator corresponds to at least one reserve stroke of the actuating part drive.
  • This additional hydraulic accumulator enables a particularly energy-saving operation of the supply device, because the electric motors that drive the pumps, in particular when maintaining a position, can be switched off temporarily.
  • the hydraulic accumulators are preferably designed as piston accumulators. Piston accumulators are distinguished by a high degree of gas tightness. More preferably, piston accumulators having welded covers are used.
  • the piston accumulator can be monitored very easily during running operation, because the pressure on the gas side corresponds to the pressure on the fluid side. The calculation is based on real gas laws. For detecting the gas state quantities of pressure (p), volume (V), and temperature (T), the above-mentioned displacement device for measurement of the oil pressure on the cylinder stroke and thus of the pressure gradient can be used, as can the other sensors that are connected to the second medium space.
  • a plurality of hydraulic accumulators can be connected in parallel, in order to enhance the failure safety through redundancy on one hand and increase the capacity on the other.
  • a fluid discharge line can be connected to the first medium space; the fluid discharge line can be actively locked by a safety controller with a safety valve, and permits discharging of the fluid in the direction of the tank.
  • the fluid pressure in the first medium space can be released in a controlled manner through a safety controller, preferably with an interchangeable control valve assembly and a safety valve, in the blocked position, the outflow of fluid from the first medium space is prevented by the fluid discharge line, such that a pressure build-up is enabled in the first place.
  • the release from the first medium space takes place in accordance with the closed circuit principle.
  • the safety controller can be triggered by a control valve assembly in n-out-of-m (n-oo-m) logic, preferably by a control valve assembly in a 1-oo-2 logic or 2-oo-3 logic.
  • a 1-oo-2 logic at least one logical unit of two must be switched off in order to open the safety valve.
  • 2-oo-3 logic at least two logical units must be switched off in order to open the safety valve.
  • the safety valve assembly is advantageously interchangeable, in order to be able to equip the turbine valve actuator optionally with a control valve assembly of the 1-oo-2 logic or the 2-oo-3 logic and even be able to interchange these with one another later.
  • the safety valve assembly enables a partial stroke test expediently. An embodiment of the 2-oo-3 logic with a partial stroke test is described in the above-mentioned patent document. DE 10 2004 042 891 83.
  • FIGS. 1 to 3 illustrate schematic diagrams for three embodiments of the turbine valve actuator according to the invention
  • FIGS. 4 and 5 illustrate two perspective views of a turbine valve actuator according to a third embodiment of the invention, which are rotated 180° from one another;
  • FIG. 6 illustrates a block diagram of a controller of a turbine valve actuator according to the invention.
  • FIG. 7 illustrates a comparison of possible, producible force-stroke characteristics of the actuating part.
  • FIGS. 1 to 3 illustrate three embodiments of turbine valve actuators 100 , 200 , 300 according to the invention, for driving at least one valve unit (not shown) of a medium-operated consumer unit, such as a steam or gas turbine, having an actuating part drive 102 , 202 , 302 , which comprises a movable actuating part 104 , 204 , 304 , a first medium space 106 , 206 , 306 , and a second medium space 108 , 208 , 308 .
  • a medium-operated consumer unit such as a steam or gas turbine
  • a pressure build-up in the first medium space 106 , 206 , 306 attempts to cause movement of the actuating part 104 , 204 , 304 in a first direction R, and a pressure build-up in the second medium space 108 , 208 , 308 attempts to cause movement of the actuating part 104 , 204 , 304 in an opposing second direction GR.
  • the first medium space 106 , 206 , 306 can be supplied with a fluid in predeterminable amounts by means of a supply device 110 , 210 , 310 .
  • the second medium space 108 , 208 , 308 is acted upon by an energy accumulator 112 , 212 , 312 .
  • the energy accumulator is, according to the invention, a hydraulic accumulator 112 , 212 , 312 provided with a pre-load pressure, which is permanently connected to the second medium space 108 , 208 , 308 .
  • the actuating part drive 102 , 202 , 302 is formed by a hydraulic working cylinder 114 , 214 , 314 .
  • the first medium space 106 , 206 , 306 forms a rod working space
  • the second medium space 108 , 208 , 308 forms a piston working space within a cylinder housing 116 , 216 , 316 , the spaces formed being separated from one another by a piston rod unit as an actuating part 104 , 204 , 304 .
  • the hydraulic working cylinder 114 , 214 , 314 is constructed such that an extension of the piston rod unit 104 , 204 , 304 causes a closing of a downstream valve unit, so that a mass flow of stream to a medium-operated consumer unit is interrupted, To close the valve unit in a fail-safe operation, the piston rod unit 104 , 204 , 304 therefore extends due to the pre-load pressure of the hydraulic accumulator 112 , 212 , 312 relative to the cylinder housing 116 , 216 , 316 , if the fluid pressure falls in the first medium space 106 , 206 , 306 .
  • the first medium space 106 , 206 , 306 can be supplied with the supply unit 110 , 210 , 310 , which cooperates with a positioning device 117 , 217 , 317 .
  • an axial piston pump 120 , 320 having a swivel angle adjustment can be driven with an electric motor 118 , 218 , 318 .
  • the axial piston pump 120 , 320 draws fluid out from a tank T.
  • the tank T comprises a temperature sensor 122 , 222 , 322 and a fill level sensor 124 , 224 , 324 .
  • the fluid is forced through a filter 126 , 226 , 326 on the way to a proportional valve 128 , 328 .
  • the proportional valve 128 , 328 of the positioning device 117 , 217 , 317 which is conceived as a 4/3-way valve, or operated as a 3/3-way valve, the first medium space 106 , 206 , 306 can be supplied with fluid.
  • the pressure in the first medium space 106 , 206 , 306 may, however, also be maintained.
  • the proportional valve 128 , 328 permits a discharging of the first medium space 106 , 206 , 306 in the direction of the tank T via a fluid line 129 , 229 , 329 .
  • an additional hydraulic accumulator 130 , 230 , 330 is connected as a buffer accumulator.
  • the fluid pressure in the line 132 , 232 , 332 which leads to the additional hydraulic, accumulator 130 , 230 , 330 , is monitored via a pressure sensor 134 , 234 , 334 .
  • a pressure adjustment device 136 , 236 , 336 is Also connected to this line 132 , 232 , 332 .
  • the pressure adjustment device 136 , 236 , 336 comprises a fluid line 137 , 237 , 337 to the tank T for relieving the second medium space 108 , 208 , 308 .
  • the fluid pressure in the second medium space 108 , 208 , 308 can be adjusted to a minimum pressure in such a manner that the actuating part 104 , 204 , 304 moves in the unpressurized first medium space 106 , 206 , 306 in the second direction GR to an end position.
  • This minimum pressure corresponds at least to the minimum actuating force of the actuating part drive 102 , 202 , 302 at the extended actuating part 104 , 204 , 304 .
  • the pressure in the second medium space 108 , 208 , 308 of the working cylinder 114 , 214 , 314 rises.
  • the maximum pressure in the second medium space 108 , 208 , 308 is, however, limited by the pressure adjustment device 136 , 236 , 336 .
  • a fluid discharge line 138 , 238 , 338 from the first medium space 106 , 206 , 306 in the direction of the tank T is provided.
  • This fluid discharge line 138 , 238 , 338 can be actively locked by a safety controller 140 , 240 , 340 having a control valve assembly in a n-oo-m logic 141 , 241 , 341 and a safety valve 142 , 242 , 342 .
  • the safety controller 140 , 240 , 340 ensures that the downstream valve unit is only opened if the safety valve 142 , 242 , 342 is actively locked, because only then can a pressure build-up take place in the first medium space 106 , 206 , 306 .
  • the pre-load pressure on a gas side 144 , 244 , 344 of a hydraulic accumulator 112 , 212 , 312 is adjusted by a pre-load adjustment device 146 , 246 , 346 .
  • the positioning device 127 , 227 , 327 , the pressure adjustment device 136 , 236 , 336 , and optionally the pre-load adjustment device 146 , 246 , 346 receive position set-point targets x soll ( FIG. 6 ) or actual position values x ist from a (central or remote) controller 148 , 248 , 348 for the respective medium spaces 106 , 108 ; 206 , 208 ; 306 , 308 , so that different force-stroke characteristics of the actuating parts 104 , 204 , 304 can be realized, as shall be described in greater detail below.
  • the position of the piston rod unit 104 , 204 , 304 can be detected with a displacement measurement device 150 , 250 , 350 .
  • the displacement measurement device 150 , 250 , 350 comprises a sensor 152 , 252 , 352 on a rear side 154 , 254 , 354 of the working cylinder 114 , 214 , 314 ; this sensor detects the position of the piston rod unit 104 , 204 , 304 via a rod 156 , 256 , 356 coupled to the piston rod unit 104 , 204 , 304 .
  • a pressure sensor 158 , 258 , 358 and a temperature sensor 160 , 260 , 360 are connected to the second medium space IDS, 208 , 308 .
  • non-contact limit switches 162 , 164 ; 262 , 264 ; 362 , 364 for monitoring the position of the piston rod unit 104 , 204 , 304 in the working cylinder 114 , 214 , 314 are provided. All of the sensors are coupled to the central or remote controller 148 , 248 , 348 .
  • a cooling unit 166 , 266 , 366 is provided in order to cool the turbine valve actuator 100 , 200 , 300 and the circulating fluid.
  • the working cylinder 114 , 214 , 314 and the fluid are tempered by a self-sufficient, self-contained refrigeration cycle. Water-glycol is used as the operating medium.
  • the cylinder bottom 168 , 268 , 368 of the working cylinder 114 , 214 , 314 is provided with cooling channels.
  • the tank T comprises cooling coils, fn this manner, the external heat output from the valve unit into the fluid at the entry point is reduced. Heat is exchanged with the ambient air by means of a cooling air blower 369 ( FIG. 4 ).
  • the electrical components are coupled via a terminal board 170 , 270 , 370 .
  • the embodiment of FIG. 2 differs from the embodiment of FIG. 1 only in that the supply device 210 comprises a gear pump 220 having a constant delivery volume, instead of an axial piston pump 120 .
  • a positioning device 217 comprises a direction-switching valve 228 instead of a proportional valve 128 .
  • FIG. 3 illustrates an embodiment of the turbine valve actuator 300 in particular for diverter valves.
  • This embodiment is based on the embodiment of FIG. 1 and comprises a working cylinder 314 with which the piston rod unit 304 in the second medium space 308 comprises an extension 372 , which extends through a cylinder bottom 368 of the working cylinder 314 .
  • the surface 374 of the piston rod unit 304 in the second medium space 308 that can be acted upon with fluid is reduced.
  • FIGS. 4 and 5 illustrate the structure of the turbine valve actuator 300 in perspective views, which are rotated 180° to one another.
  • the working cylinder 314 is fastened therein by means of a flange plate 376 on a valve unit.
  • the components of the actuating part drive are compactly disposed within narrow installation space boundaries 380 , wherein the hydraulic accumulator 312 and the additional hydraulic accumulator 330 are embodied as redundant piston accumulators with a welded lid.
  • the electric motor 318 for driving the axial piston pump 320 can be seen.
  • a cooling unit 336 comprising the cooling air blower 369 is disposed laterally.
  • Below the cooling unit 366 is the safety controller 340 .
  • the proportional valve 328 is disposed below the turbine valve actuator 300 .
  • a fluid collecting tray 328 for the fluid with a monitoring contact 384 is disposed.
  • FIG. 6 illustrates an exemplary block diagram of the control of the components of the turbine valve actuator 100 .
  • the central or remote controller 148 prescribes a position set-point value x soll , which is compared with a position sensor 152 of the displacement measurement device 150 for the piston rod unit 104 of the working cylinder 114 .
  • a position regulator 156 of the proportional valve 128 of the positioning device 117 is controlled with the result of this comparison.
  • the proportional valve 128 either connects the first medium space 106 of the working cylinder 114 to an axial piston pump 120 , or enables a discharging of fluid in the direction of a tank T via the fluid line 129 , or the existing pressure in the first medium space 106 is kept constant.
  • the position set-point value x soll or the actual position value x ist can be translated into a pressure set-point target p soll , which then serves to control a proportional pressure valve 188 of the pressure adjustment device 136 , through which the fluid pressure in the second medium space 108 can be adjusted.
  • the pressure adjustment device 136 is also connected to the axial piston pump 120 or the tank T, thus making it possible to selectively raise or lower the pressure in the second medium space 108 .
  • the pre-load adjustment device 146 that is provided can also be supplied with a pressure target p soll and adjusts the pre-load pressure on the gas side 144 of the hydraulic accumulator 112 .
  • FIG. 7 shows that the combined use of the positioning device 117 , 217 , 317 , the pressure adjustment device 136 , 236 , 336 , and the pre-load adjustment device 146 , 246 , 346 makes it possible to implement different force-stroke characteristics 1 - 5 of the actuating part.
  • the turbine valve actuator 100 , 200 , 300 can be adjusted so as to have a degressive characteristic 1 . It is also possible to set a linear characteristic 2 , a progressive characteristic 3 , a constant (isobaric) characteristic at different levels 4 , 4 ′, or a regressive characteristic 5 .
  • the turbine valve actuator can be optimally adapted to the required force profiles, as they must be adjusted to, for example, in different operating conditions. It is thus also possible to adaptively limit force. Because the characteristic can be easily changed through a set-point target, an adjustment can be made during running operation, from a control room.
  • the turbine valve actuators 100 , 200 , 300 have various advantages, in particular a high modularity and adaptability through the external hydropneumatic springs in the form of the hydraulic accumulator 112 , 212 , 312 .
  • the modular design makes it furthermore possible to interchange or later replace the components and complete subsystems, such as, for example, the supply device 110 , 210 , 310 or the cooling unit 166 , 266 , 366 .
  • the availability can be enhanced through redundancy, e.g., the hydraulic accumulators 112 , 130 ; 212 , 230 ; 312 , 330 .
  • the turbine valve actuators 100 , 200 , 300 are further distinguished by having a high flexibility through a force level adaptation, which can be adjusted even during the operation from a control room. In this manner, different force-stroke characteristics can be adjusted to during running operation.
  • the piston accumulator types that are used entail sophisticated series components with a design for durability.
  • the high reliability of the hydraulic accumulators 112 , 130 ; 212 , 230 ; 312 , 330 is achieved through a gas-side welded cover and a low-friction sealing system.
  • the hydropneumatic springs and the redundant use of piston accumulators ensures a high reliability of the turbine valve actuator at low costs in production and in the running operation.
  • the turbine valve actuators 100 , 200 , 300 according to the invention thus possess considerable advantages over the turbine valve actuators of mechanical springs known in the prior art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention relates to a turbine valve actuator (300) for Controlling at least one valve unit of a media-operated consumer unit, such as a steam or gas turbine, having an actuating part drive (102) which has a movable actuating part (104), at least one first media space (106) and at least one second media space (108), wherein a pressure build up in the first media space (106) attempts to cause a movement of the actuating part (104) in a first direction (R) and a pressure build-up in the second media space (108) attempts to cause a movement of the actuating part (104) in an opposing second direction (GR), wherein the first media space (106) can be supplied with a fluid in predeterminable amounts by means of a supply arrangement (110) and the second media space (108) is acted upon by an energy accumulator (112). The invention is characterised in that the energy accumulator is at least one hydraulic accumulator (112) which is provided with a preload pressure and is permanently connected to the second media space (108).

Description

  • The invention relates to a turbine valve actuator for controlling at least one valve unit of a medium-operated consumer unit, such as a steam or gas turbine, having an actuating part drive that comprises a movable actuating part, at least one first medium space, and at least one second medium space, wherein a pressure build-up in the first medium space attempts to cause a movement of the actuating part in a first direction and a pressure build-up in the second medium space attempts to cause a movement of the actuating part in an opposing second direction, wherein the first medium space can be supplied with a fluid in predeterminable amounts by means of a supply device and the second medium space is acted upon by an energy accumulator.
  • Such turbine valve actuators are known in the prior art, e.g., from patent document DE 10 2004 042 891 B3. Such a turbine valve actuator is constituted of a hydraulic working cylinder, wherein a piston rod unit is permanently spring-loaded, preferably by a packet of Belleville washers. The piston rod unit is held against the compressive force of the Belleville washers via the system pressure of a fluid circuit in a retracted position. In the event of a system pressure drop, the piston rod unit extends from the working cylinder, and a control valve is activated, which controls a medium flow to a consumer unit and, in this case, stops a mass flow of steam for the driving of a steam or gas turbine.
  • In the known actuating cylinder with mechanical springs, the drive must be designed and manufactured according to the individual requirements of the individual steam valve type. A subsequent adaptation of the turbine valve actuator to another steam valve is not possible. The end result is a wide variety of types, which is associated with high costs for development, production, storage, and distribution.
  • In light of this prior art, the invention addresses the problem of providing an improved turbine valve actuator with which subsequent adaptation to other steam valves is possible.
  • This problem is solved by a turbine valve actuator having the features of claim 1. Advantageous embodiments and developments of the invention will become apparent from the dependent claims. The invention provides that the energy accumulator is at least one hydraulic accumulator provided with a pre-load pressure, which is permanently connected to the second medium space.
  • The basis of the turbine valve actuator according to the present invention is the use of at least one hydraulic accumulator in order to control same. With the solution according to the present invention, the variety of types can be reduced to a few basic types. The turbine valve actuator can therefore be connected to a wide range of valve units. The advantageous use of piston accumulators as standard components also contributes to reducing costs. Hydraulic accumulators are distinguished by the possibility of the adjustability of the characteristics thereof. The use of hydraulic accumulators that are external, i.e., arranged outside the medium spaces, makes it possible to employ interchangeable components and thus supports the modularization and adaptability of the turbine valve actuator. Another advantage is that the actuating part drive can be operated in a nearly force-free manner for installation and maintenance.
  • Advantageously, the actuating part drive is configured as a hydraulic motor or hydraulic working cylinder, in a preferred embodiment, the first medium space forms a rod working space in the hydraulic working cylinder, and the second medium space forms a piston working space within a cylinder housing, the spaces formed being separated from one another by a piston rod unit as an actuating part. Such working cylinders are readily available on the market as linear cylinders in a variety of embodiments. For the purposes of modularization, they can be used as standard components. This contributes to considerable cost savings in manufacturing. Advantageously, the working cylinder is equipped with an end position damping in the direction of extension.
  • To close the valve unit in a failsafe operation, the piston rod unit either retracts or extends due to the fluid pressure of the hydraulic accumulator, relative to the cylinder housing, if the fluid pressure drops in the first medium space. Thus, the fluid pressure is to be maintained in the first medium space if the valve unit is to be opened. If, however, the fluid pressure drops in the first medium space for any reason, e.g., because of a failure in the supply device or due to targeted release via a safety valve, then without intervention, this leads to a closing of the valve unit and thus to the shutting off of a media flow to a consumer unit downstream of the valve unit.
  • Furthermore, a pressure-adjusting device can be provided. This pressure-adjusting device makes it possible for the fluid pressure in the second medium space to be adjusted between a minimum pressure and a maximum pressure in such a manner that the actuating part moves in the unpressurized first medium space in the second direction to an end position, wherein an exceeding of the allowable driving forces is prevented. The pressure-adjusting device consequently maintains the functional readiness of the turbine valve actuator in ongoing operation. The pressure at which the actuating part is acted upon is advantageously coordinated to the downstream valve unit, thus ensuring that same is closed if there is a pressure drop in the first medium space. Due to the pressure-adjusting device, an overload protector for the valve unit is also provided, because excess pressures in the second medium space can be prevented by releasing the fluid.
  • Furthermore, the pre-load pressure can also be adjusted on a gas side of the hydraulic accumulator, by using a pre-load adjustment device. Adjusting the pre-load pressure makes it possible to adjust different spring characteristics or pressure levels for these spring characteristics.
  • A positioning device, the pressure adjustment device, and/or the pre-load adjustment device preferably receive position set-point targets or actual position values for the respective medium spaces from a central or remote controller, so that different force-stroke characteristics of the actuating part can be realized, and preferably can be altered during operation of the turbine valve actuator. These targets can also be provided from a control room in running operation. Whereas safety devices known in the prior are only able to produce degressive characteristics through Belleville washers, the turbine valve actuator according to the invention now makes it possible to produce progressive, linear, constant (isobaric), or even regressive force-stroke characteristics. Thus, for example, with an isobaric characteristic, the pressure consumed from the hydraulic accumulator as an energy accumulator can be adjusted to a nearly constant level via the traveling of the actuating part, wherein different pressure levels can be advantageously selected.
  • Preferably, the pressure of the actuating part can be determined by means of a preferably integrated and/or redundant displacement measurement device, and thus the desired pressure can be defined in the second medium space. The displacement measurement here makes it possible, in a particularly simple manner, to monitor the turbine valve actuator. Furthermore, sensors for measuring the pressure and/or temperature can be provided at the second medium space. Thus, during movement of the piston rod unit, it is possible to constantly monitor the availability of closing force through the evaluation by the sensor measurement results, because all of the state variables of the hydraulic accumulator can be provided with the pressure, temperature, and derived volume.
  • Particularly advantageously, the supply device for the first medium space, in an actuating drive, comprises a pressure-controlled axial piston pump having a swivel angle adjustment, or, in a switching drive, comprises a gear pump having a constant delivery volume. The supply device cooperates with the positioning device. If the supply device comprises an axial piston pump, then a proportional valve is provided in the positioning device. If the supply device comprises a gear pump, then the positioning device has a control valve. To conserve energy, the gear pump can be switched off after a desired pressure is reached and switched on only when needed (accumulator charging).
  • The supply device may further comprise an additional hydraulic accumulator as a part of an accumulator charge circuit. The volume accumulated in the additional hydraulic accumulator corresponds to at least one reserve stroke of the actuating part drive. This additional hydraulic accumulator enables a particularly energy-saving operation of the supply device, because the electric motors that drive the pumps, in particular when maintaining a position, can be switched off temporarily.
  • The hydraulic accumulators are preferably designed as piston accumulators. Piston accumulators are distinguished by a high degree of gas tightness. More preferably, piston accumulators having welded covers are used. The piston accumulator can be monitored very easily during running operation, because the pressure on the gas side corresponds to the pressure on the fluid side. The calculation is based on real gas laws. For detecting the gas state quantities of pressure (p), volume (V), and temperature (T), the above-mentioned displacement device for measurement of the oil pressure on the cylinder stroke and thus of the pressure gradient can be used, as can the other sensors that are connected to the second medium space.
  • Particularity advantageously, a plurality of hydraulic accumulators can be connected in parallel, in order to enhance the failure safety through redundancy on one hand and increase the capacity on the other.
  • A fluid discharge line can be connected to the first medium space; the fluid discharge line can be actively locked by a safety controller with a safety valve, and permits discharging of the fluid in the direction of the tank. Thus, the fluid pressure in the first medium space can be released in a controlled manner through a safety controller, preferably with an interchangeable control valve assembly and a safety valve, in the blocked position, the outflow of fluid from the first medium space is prevented by the fluid discharge line, such that a pressure build-up is enabled in the first place. The release from the first medium space takes place in accordance with the closed circuit principle. The safety controller can be triggered by a control valve assembly in n-out-of-m (n-oo-m) logic, preferably by a control valve assembly in a 1-oo-2 logic or 2-oo-3 logic. In a 1-oo-2 logic, at least one logical unit of two must be switched off in order to open the safety valve. In a 2-oo-3 logic, at least two logical units must be switched off in order to open the safety valve. The safety valve assembly is advantageously interchangeable, in order to be able to equip the turbine valve actuator optionally with a control valve assembly of the 1-oo-2 logic or the 2-oo-3 logic and even be able to interchange these with one another later. The safety valve assembly enables a partial stroke test expediently. An embodiment of the 2-oo-3 logic with a partial stroke test is described in the above-mentioned patent document. DE 10 2004 042 891 83.
  • It is further possible to use preferably non-contact limit switches for monitoring the piston rod unit in the cylinder housing.
  • The invention shall be described in greater detail below, with reference to the embodiments illustrated in the drawings.
  • FIGS. 1 to 3 illustrate schematic diagrams for three embodiments of the turbine valve actuator according to the invention;
  • FIGS. 4 and 5 illustrate two perspective views of a turbine valve actuator according to a third embodiment of the invention, which are rotated 180° from one another;
  • FIG. 6 illustrates a block diagram of a controller of a turbine valve actuator according to the invention; and
  • FIG. 7 illustrates a comparison of possible, producible force-stroke characteristics of the actuating part.
  • FIGS. 1 to 3 illustrate three embodiments of turbine valve actuators 100, 200, 300 according to the invention, for driving at least one valve unit (not shown) of a medium-operated consumer unit, such as a steam or gas turbine, having an actuating part drive 102, 202, 302, which comprises a movable actuating part 104, 204, 304, a first medium space 106, 206, 306, and a second medium space 108, 208, 308. A pressure build-up in the first medium space 106, 206, 306 attempts to cause movement of the actuating part 104, 204, 304 in a first direction R, and a pressure build-up in the second medium space 108, 208, 308 attempts to cause movement of the actuating part 104, 204, 304 in an opposing second direction GR. The first medium space 106, 206, 306 can be supplied with a fluid in predeterminable amounts by means of a supply device 110, 210, 310. The second medium space 108, 208, 308 is acted upon by an energy accumulator 112, 212, 312. The energy accumulator is, according to the invention, a hydraulic accumulator 112, 212, 312 provided with a pre-load pressure, which is permanently connected to the second medium space 108, 208, 308.
  • The actuating part drive 102, 202, 302 is formed by a hydraulic working cylinder 114, 214, 314. In the hydraulic working cylinder 114, 214, 314, the first medium space 106, 206, 306 forms a rod working space, and the second medium space 108, 208, 308 forms a piston working space within a cylinder housing 116, 216, 316, the spaces formed being separated from one another by a piston rod unit as an actuating part 104, 204, 304. The hydraulic working cylinder 114, 214, 314 is constructed such that an extension of the piston rod unit 104, 204, 304 causes a closing of a downstream valve unit, so that a mass flow of stream to a medium-operated consumer unit is interrupted, To close the valve unit in a fail-safe operation, the piston rod unit 104, 204, 304 therefore extends due to the pre-load pressure of the hydraulic accumulator 112, 212, 312 relative to the cylinder housing 116, 216, 316, if the fluid pressure falls in the first medium space 106, 206, 306.
  • The first medium space 106, 206, 306 can be supplied with the supply unit 110, 210, 310, which cooperates with a positioning device 117, 217, 317. As illustrated in FIGS. 1 and 3, an axial piston pump 120, 320 having a swivel angle adjustment can be driven with an electric motor 118, 218, 318. The axial piston pump 120, 320 draws fluid out from a tank T. For safety, the tank T comprises a temperature sensor 122, 222, 322 and a fill level sensor 124, 224, 324. The fluid is forced through a filter 126, 226, 326 on the way to a proportional valve 128, 328. With the proportional valve 128, 328 of the positioning device 117, 217, 317, which is conceived as a 4/3-way valve, or operated as a 3/3-way valve, the first medium space 106, 206, 306 can be supplied with fluid. The pressure in the first medium space 106, 206, 306 may, however, also be maintained. In the crossed setting, the proportional valve 128, 328 permits a discharging of the first medium space 106, 206, 306 in the direction of the tank T via a fluid line 129, 229, 329. Between the filter 126, 226, 326 and the proportional valve 128, 328, an additional hydraulic accumulator 130, 230, 330 is connected as a buffer accumulator. The fluid pressure in the line 132, 232, 332, which leads to the additional hydraulic, accumulator 130, 230, 330, is monitored via a pressure sensor 134, 234, 334.
  • Also connected to this line 132, 232, 332 is a pressure adjustment device 136, 236, 336, with which it is possible to adjust the fluid pressure in the second medium space 108, 208, 308. The pressure adjustment device 136, 236, 336 comprises a fluid line 137, 237, 337 to the tank T for relieving the second medium space 108, 208, 308. With the pressure adjustment device 136, 236, 336, the fluid pressure in the second medium space 108, 208, 308 can be adjusted to a minimum pressure in such a manner that the actuating part 104, 204, 304 moves in the unpressurized first medium space 106, 206, 306 in the second direction GR to an end position. This minimum pressure corresponds at least to the minimum actuating force of the actuating part drive 102, 202, 302 at the extended actuating part 104, 204, 304. Upon retraction of the actuating part 104, 204, 304, the pressure in the second medium space 108, 208, 308 of the working cylinder 114, 214, 314 rises. The maximum pressure in the second medium space 108, 208, 308 is, however, limited by the pressure adjustment device 136, 236, 336.
  • Furthermore, a fluid discharge line 138, 238, 338 from the first medium space 106, 206, 306 in the direction of the tank T is provided. This fluid discharge line 138, 238, 338 can be actively locked by a safety controller 140, 240, 340 having a control valve assembly in a n-oo- m logic 141, 241, 341 and a safety valve 142, 242, 342. The safety controller 140, 240, 340 ensures that the downstream valve unit is only opened if the safety valve 142, 242, 342 is actively locked, because only then can a pressure build-up take place in the first medium space 106, 206, 306.
  • The pre-load pressure on a gas side 144, 244, 344 of a hydraulic accumulator 112, 212, 312 is adjusted by a pre-load adjustment device 146, 246, 346.
  • The positioning device 127, 227, 327, the pressure adjustment device 136, 236, 336, and optionally the pre-load adjustment device 146, 246, 346 receive position set-point targets xsoll (FIG. 6) or actual position values xist from a (central or remote) controller 148, 248, 348 for the respective medium spaces 106, 108; 206, 208; 306, 308, so that different force-stroke characteristics of the actuating parts 104, 204, 304 can be realized, as shall be described in greater detail below.
  • Various sensors are provided in order to monitor the turbine valve actuator 100, 200, 300. The position of the piston rod unit 104, 204, 304 can be detected with a displacement measurement device 150, 250, 350. The displacement measurement device 150, 250, 350 comprises a sensor 152, 252, 352 on a rear side 154, 254, 354 of the working cylinder 114, 214, 314; this sensor detects the position of the piston rod unit 104, 204, 304 via a rod 156, 256, 356 coupled to the piston rod unit 104, 204, 304. In addition, a pressure sensor 158, 258, 358 and a temperature sensor 160, 260, 360 are connected to the second medium space IDS, 208, 308. Additionally, non-contact limit switches 162,164; 262, 264; 362, 364 for monitoring the position of the piston rod unit 104, 204, 304 in the working cylinder 114, 214, 314 are provided. All of the sensors are coupled to the central or remote controller 148, 248, 348.
  • In order to cool the turbine valve actuator 100, 200, 300 and the circulating fluid, a cooling unit 166, 266, 366 is provided. The working cylinder 114, 214, 314 and the fluid are tempered by a self-sufficient, self-contained refrigeration cycle. Water-glycol is used as the operating medium. The cylinder bottom 168, 268, 368 of the working cylinder 114, 214, 314 is provided with cooling channels. The tank T comprises cooling coils, fn this manner, the external heat output from the valve unit into the fluid at the entry point is reduced. Heat is exchanged with the ambient air by means of a cooling air blower 369 (FIG. 4).
  • The electrical components are coupled via a terminal board 170, 270, 370.
  • The embodiment of FIG. 2 differs from the embodiment of FIG. 1 only in that the supply device 210 comprises a gear pump 220 having a constant delivery volume, instead of an axial piston pump 120. A positioning device 217 comprises a direction-switching valve 228 instead of a proportional valve 128.
  • FIG. 3 illustrates an embodiment of the turbine valve actuator 300 in particular for diverter valves. This embodiment is based on the embodiment of FIG. 1 and comprises a working cylinder 314 with which the piston rod unit 304 in the second medium space 308 comprises an extension 372, which extends through a cylinder bottom 368 of the working cylinder 314. In this manner, the surface 374 of the piston rod unit 304 in the second medium space 308 that can be acted upon with fluid is reduced.
  • FIGS. 4 and 5 illustrate the structure of the turbine valve actuator 300 in perspective views, which are rotated 180° to one another. The working cylinder 314 is fastened therein by means of a flange plate 376 on a valve unit. The components of the actuating part drive are compactly disposed within narrow installation space boundaries 380, wherein the hydraulic accumulator 312 and the additional hydraulic accumulator 330 are embodied as redundant piston accumulators with a welded lid. In addition, the electric motor 318 for driving the axial piston pump 320 can be seen. A cooling unit 336 comprising the cooling air blower 369 is disposed laterally. Below the cooling unit 366 is the safety controller 340. In the control block next to the safety controller 340, the proportional valve 328 is disposed. Below the turbine valve actuator 300, a fluid collecting tray 328 for the fluid with a monitoring contact 384 is disposed.
  • FIG. 6 illustrates an exemplary block diagram of the control of the components of the turbine valve actuator 100. The central or remote controller 148 prescribes a position set-point value xsoll, which is compared with a position sensor 152 of the displacement measurement device 150 for the piston rod unit 104 of the working cylinder 114. A position regulator 156 of the proportional valve 128 of the positioning device 117 is controlled with the result of this comparison. The proportional valve 128 either connects the first medium space 106 of the working cylinder 114 to an axial piston pump 120, or enables a discharging of fluid in the direction of a tank T via the fluid line 129, or the existing pressure in the first medium space 106 is kept constant. Furthermore, the position set-point value xsoll or the actual position value xist can be translated into a pressure set-point target psoll, which then serves to control a proportional pressure valve 188 of the pressure adjustment device 136, through which the fluid pressure in the second medium space 108 can be adjusted. The pressure adjustment device 136 is also connected to the axial piston pump 120 or the tank T, thus making it possible to selectively raise or lower the pressure in the second medium space 108. Additionally, the pre-load adjustment device 146 that is provided can also be supplied with a pressure target psoll and adjusts the pre-load pressure on the gas side 144 of the hydraulic accumulator 112.
  • FIG. 7 shows that the combined use of the positioning device 117, 217, 317, the pressure adjustment device 136, 236, 336, and the pre-load adjustment device 146, 246, 346 makes it possible to implement different force-stroke characteristics 1-5 of the actuating part. Analogously to Belleville washers, the turbine valve actuator 100, 200, 300 can be adjusted so as to have a degressive characteristic 1. It is also possible to set a linear characteristic 2, a progressive characteristic 3, a constant (isobaric) characteristic at different levels 4, 4′, or a regressive characteristic 5. Thus, the turbine valve actuator can be optimally adapted to the required force profiles, as they must be adjusted to, for example, in different operating conditions. It is thus also possible to adaptively limit force. Because the characteristic can be easily changed through a set-point target, an adjustment can be made during running operation, from a control room.
  • The turbine valve actuators 100, 200, 300 according to the invention have various advantages, in particular a high modularity and adaptability through the external hydropneumatic springs in the form of the hydraulic accumulator 112, 212, 312. The modular design makes it furthermore possible to interchange or later replace the components and complete subsystems, such as, for example, the supply device 110, 210, 310 or the cooling unit 166, 266, 366. There is lower driving variant diversity, and many identical parts can be used. The availability can be enhanced through redundancy, e.g., the hydraulic accumulators 112, 130; 212, 230; 312, 330. The turbine valve actuators 100, 200, 300 are further distinguished by having a high flexibility through a force level adaptation, which can be adjusted even during the operation from a control room. In this manner, different force-stroke characteristics can be adjusted to during running operation. The piston accumulator types that are used entail sophisticated series components with a design for durability. The high reliability of the hydraulic accumulators 112, 130; 212, 230; 312, 330 is achieved through a gas-side welded cover and a low-friction sealing system. The hydropneumatic springs and the redundant use of piston accumulators ensures a high reliability of the turbine valve actuator at low costs in production and in the running operation. In all, the turbine valve actuators 100, 200, 300 according to the invention thus possess considerable advantages over the turbine valve actuators of mechanical springs known in the prior art.

Claims (12)

1. A turbine valve actuator for controlling at least one valve unit of a medium-operated consumer unit such as a steam or gas turbine, having an actuating part drive (102, 202, 302) that comprises a movable actuating part (104, 204, 304), at least one first medium space (106, 206, 306), and at least one second medium space (108, 208, 308), wherein a pressure build-up in the first medium space (106, 206, 306) attempts to cause a movement of the actuating part (104, 204, 304) in a first direction (R) and a pressure build-up in the second medium space (108, 208, 308) attempts to cause a movement of the actuating part (104, 204, 304) in an opposing second direction (GR), wherein the first medium space (106, 206, 306) can be supplied with a fluid in predeterminable amounts by means of a supply device (110, 210, 310) and the second medium space (108, 208, 308) is acted upon by an energy accumulator (112, 212, 312), characterized in that the energy accumulator is at least one hydraulic accumulator (112, 212, 312) provided with a pre-load pressure, which is permanently connected to the second medium space (108, 208, 308).
2. The turbine valve actuator according to claim 1, characterized in that the actuating part drive (102, 202, 302) is formed by a hydraulic motor or a hydraulic working cylinder (114, 214, 314).
3. The turbine valve actuator according to claim 2, characterized in that, in the hydraulic working cylinder (114, 214, 314), the first medium space (106, 206, 306) forms a rod working space and the second medium space (108, 208, 308) forms a piston working space within a cylinder housing (116, 216, 316), the spaces formed being separated from one another by the piston rod unit as the actuating part (104, 204, 304).
4. The turbine valve actuator according to claim 3, characterized in that, to close the valve unit in a fail-safe operation, the piston rod unit (104, 204, 304) extends or retracts due to the fluid pressure of the hydraulic accumulator (112, 212, 312) relative to the cylinder housing (116, 216, 316), if the fluid pressure drops in the first medium space (106, 206, 306).
5. The turbine valve actuator according to claim 1, characterized in that, with a pressure-adjusting device (136, 236, 336), it is possible for the fluid pressure in the second medium space (108, 208, 308) to be adjusted between a minimum pressure and a maximum pressure in such a manner that the actuating part (104, 204, 304) moves in the unpressurized first medium space (106, 206, 306) in the second direction (GR) to an end position, wherein an exceeding of the allowable driving forces is prevented.
6. The turbine valve actuator according to claim 1, characterized in that, with a pre-load adjustment device (146, 246, 346), the pre-load pressure on a gas side (144, 244, 344) of the hydraulic accumulator (112, 212, 312) can be adjusted.
7. The turbine valve actuator according to claim 1, characterized in that a positioning device (117, 217, 317), the pressure adjustment device (136, 236, 336), and/or the pre-load adjustment device (146, 246, 346) receive position set-point targets (xsoll) or actual position values (xist) from a central or remote controller (148, 248, 348) for the respective medium spaces (106, 108; 206, 208; 306, 308), so that different force-stroke characteristics (1-5) of the actuating part (104, 204, 304) can be realized, and preferably can be altered during the operation of the turbine valve actuator.
8. The turbine valve actuator according to claim 7, characterized in that the pressure consumed from the hydraulic accumulator (112, 212, 312) as an energy accumulator can be adjusted to a nearly constant level (4,4′) (isobaric) via the travel of the actuating part (104, 204, 304).
9. The turbine valve actuator according to claim 1, characterized in that, by means of a displacement measurement device (150, 250, 350), the position of the actuating part (104, 204, 304) can be detected and thus the desired pressure in the second medium space (108, 208, 308) can be determined.
10. The turbine valve actuator according to claim 1, characterized in that the supply device (110, 210, 310) for the first medium space (106, 206, 306) comprises an axial piston pump (120, 320) having a swivel angle adjustment, or a gear pump (220) having a constant delivery volume in an accumulator charging, and the positioning device (117, 217, 317) comprises a proportional valve (128, 328) or a control valve (228).
11. The turbine valve actuator according to claim 1, characterized in that a fluid pressure in the first medium space (106, 206, 306) can be relieved in a controlled manner through a safety controller (140, 240, 340), preferably with an interchangeable control valve assembly (141, 241, 341) and a safety valve (142, 242, 342).
12. The turbine valve actuator according to claim 11, characterized in that the control valve assembly (141, 241, 341) is embodied in a n-oo-m logic, preferably in a 1-oo-2 logic or in a 2-oo-3 logic, and further preferably allows for a partial stroke test.
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US10066645B2 (en) 2018-09-04
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EP2923089B1 (en) 2019-12-18
CN104854353B (en) 2017-04-12
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WO2014079528A1 (en) 2014-05-30
EP2923089A1 (en) 2015-09-30

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